Servo motor



A ril 21, 1964 R. D. PORTER ETAL SERVO MOTOR 3 Sheets-Sheet 2 Original Filed June 3, 1960 April 21, 1964 R. D. PORTER ETAL SERVO MOTOR 3 Sheets-Sheet 3 Original Filed June's, 1960 INVENTORS ROBERT D. PORTER CHARLES F: STEARNS W .lllll- United States Patent Of ,5 3,129,643 Patented Apr. 21, 1964 11 Ciaims. (Cl. 91382) This invention relates to fuel controls and more specifically to a fuel control for a gas turbine engine.

This is a divisional application of application Ser. No. 33,822, now abandoned, filed on June 3, 1960, entitled Fuel Control by Robert D. Porter et al.

The type of fuel control to be described herein is a modification of the type shown in Patent No. 2,822,666 issued on February 11, 1958, entitled Turbine Power Plant Fuel Control Utilizing Speed, Temperature and Compressor Pressure by S. G. Best, and reflects an improvement thereof. In the foregoing patent, for example, a separate speed-sensing device has been employed to give acceleration schedule and another speed-sensing device for state engine operating conditions. In the present invention a number of servo devices and mechanical connections have been eliminated providing a simplified and less expensive fuel control which has been made possible because of the arrangement and improvement afforded by novel features incorporated in this fuel control. The advantages which will become more apparent have been achieved without sacrificing accuracy, reliability and functionality of the fuel control all being essential factors for proper engine operation. As it is generally well-known, fuel controls of this type have been tailor made to fit a particular engine. That is to say, a control designed for an engine manufactured by one concern would not be readily adaptable to an engine manufactured by another concern and even different engines manufactured by the same concern would not lend themselves for adaptation by the same control. In this regard, the flexibility obtainable by the arrangement of these parts has made this control adaptable to a number of engines so long as the physical envelope is susceptible for such adaptation. This is made possible without incurring a costly redesign of these controls which has heretofore been the practice employed throughout the industry. Reasons for the flexibility inherent in this fuel control are due to the novel features that we employ, which are namely, the manner in which the adding bar is adapted to receive various engine-operating parameters or variables, conversion of these signals into throttle valve position, and the manner of inclusion of a three-dimensional cam and piston combination. This three-dimensional cam is designed and located with relation to its cooperating parts in such a fashion that the fuel control can be readily adapted to be incorporated into various engines without altering the relationship and functions of the other sensing and computing units incidental to the fuel control.

It is a further object of this invention to provide in the fuel control, as described, a three-dimensional cam which is made integral with a double-actual piston.

It is still a further object of this invention to provide a simplified feedback system employed with a signal generating mechanism which is capable of affording simplified means for producing either a linear or nonlinear output signal commensurate with an input signal fed into said signal generating mechanism.

These and other objects of this invention will become readily apparent from the following detailed description of the drawing in which:

FIG. 1 is a schematic illustration of a turbo power plant showing a schematically indicated fuel control operatively connected thereto.

FIG. 2 is a diagrammatic illustration of the fuel control of this invention arranged for a turbojet power plant.

FIG. 3 is a cross-sectional fragmentary view taken along the line 3-3 of FIG. 2.

FIG. 4 is a fragmentary cross-sectional view taken along line CC of FIG. 3 and also showing diagrammatically the temperature sensing mechanism of this invention.

FIG. 5 is a diagrammatic showing of the mechanism adapted to the fuel control of this invention for a turboprop power plant for driving a helicopter aircraft.

FIG. 6 is a diagrammatic showing of the mechanism adapted to the fuel control of this invention for a turboprop power plant for driving a propeller aircraft.

FIG. 7 is an illustration of engine operating curves and a random showing of a family of droop lines.

Referring particularly to FIG. 1, a gas turbine power plant is generally indicated at 10 comprising an air inlet 12, a compressor 14, a combustion section or burner chamber 16, a first turbine 18 and a second turbine 20. Turbine 18 is arranged to drive compressor 14 and turbine 2b is arranged to drive the gears located in gear box 22. Shaft 24 is illustrated as being driven by gear box 22 for driving a variable load as, for example, a heli copter rotor (not shown). It should be understood that a propeller can be adapted to be driven by this power plant in a manner well known in the art as, for example, connecting a propeller shaft directly to the gear box. In the case of a turbojet engine, the shaft may be connected directly to another set of compressor blades. Since, as is shown, turbine 20 is not directly connected to compressor or gas generator 14 which may be the case for the turboprop power plant and since the only connection between the first and second turbines is the fluid connection or the aerodynamic coupling, it is referred to as the free turbine, and the rpm. of turbine 20 and the variable load such as a helicopter rotor or propeller driven by this turbine is hereinafter referred to as (N;). Since turbine 16 is mechanically connected to the compressor or gas generator 14, it is referred to as the gas generator turbine and the rpm. of the compressor and turbine 18 driving this compressor will hereinafter be referred to as (N It will be understood that since both turbines are connected to the compressor in the case of a turbojet, there will be no distinction made between a gas generator turbine and a free turbine.

A better understanding of the general theory of the operation of fuel controls of this type is clearly illustrated in US. Patent No. 2,822,666 supra. Suffice it to say that basically, fuel control operation is a combination of me tering devices and computation mechanism controlling the quantity of fuel to the engine in the amount defining a particular schedule selected to allow the engine to operate within its safe operating limits and yet provide eflicient and optimum power plant operating conditions. Fundamentally, the fuel control functions to automatically adjust the quantity of fuel metered to the engine in accordance with the thrust required by the pilot (i.e. the position of the power lever) in such a manner as to pro vide eflicient and safe engine operating conditions. By rotation of the power lever, a signal of the desired speed is fed into the governor. This signal may be biased by the compressor inlet pressure so as to obtain the optimum speed at various altitude conditions. These signals are combined into an adding bar which compares the actual speed of the compressor with the desired speed as set by the pilot lever and feeds the resultant signal into the multiplication mechanism. The desired speed, of course, may be biased by the compressor inlet pressure or temperature. The signal which is being fed into the multiplication device for convenience is considered as the multiplicand and as will be more fully explained hereinafter, this multiplicand may be modified in accordance with various engine parameters or variables in order to automatically control the engine for all operating conditions. That is to say, the fuel control must provide sufiicient fuel to maintain the desired thrust yet prevent overtemperature, surge, or rich and lean blowouts (the effect of ratio of fuel to air). It is important to realize that the multiplicand is rated in terms of ratio units, that is to say, the value of this variable is in terms of the weight of the fuel per unit time divided by the compressor discharge pressure. (Other engine pressures may be used, but this one is preferred because of design considerations.) By relating all the controlling parameters or variables in this manner, it is now possible to multiply this ratio, hereinafter referred to as (W /P), by actual compressor discharge pressure (CDP) which in turn will give the necessary fuel flow, i.e., W /PXP=W,. Since the pressure drop across the throttle or metering valve is maintained at a constant value, a discreet positioning thereof will give a predetermined flow. As mentioned above, a distinct and important feature of our fuel control is the fact that by minor adjustments and modifications, the fuel control can be easily adapted for turboprop engines. As shown in FIG. 1, numeral 1?; schematically illustrates the control for turboprop adaptation for both a helicopter or propeller-driven aircraft. In the case of controlling a helicopter, a collective pitch control schematically shown at numeral 21 may be employed to bias the fuel control. An explanation of collective pitch is not deemed necessary to understand this invention, but a description of a suitable collective pitch control is fully illustrated in US. application Serial No. 861,396, filed December 22, 1959, for Collective Pitch Bias, assigned to the same assignee. For propellor application, control 13 is slightly modified so as to essentially retain the identical parts as used for helicopter application. Fuel control 22 senses the value of the same variables or parameters of power plant operation Whether utilized with a turbojet or a turboprop. As shown in FIG. 1, fuel control 22 senses the (N compressor inlet temperature, compressor inlet pressure and compressor discharge pressure. A pilots control gears 30 and 32 are operatively connected to the fuel control 22 for proper selection of the desired speed. Fuel is pressurized by pump 25, which may be driven by compressor 14, prior to entering the fuel control which meters or regulates the quantity of fuel fed to the fuel nozzles by line 26 for engine consumption.

Referring more particularly to FIG. 2, the fuel metering system is best described as having an inlet chamber 40 which may include screens 42 and 44 which are utilized for removing foreign matter entrained in the fuel. Screens 42 and 44 are biased downward by spring 46 which permits the screens to unseat should the pressure in inlet chamber 4% build up as a result of the screens becoming clogged. Fuel is delivered via line 48 to the throttle valve which is generally indicated by numeral 54 and is metered or regulated through metering port 52 to the engine via line 54. In order to obtain high pressure fluid for the various servo actuating devices and controls, a T-connection 56 in inlet chamber 40 is provided. It is to be noted that the pressure for servo actuation is equivalent to the pressure downstream of the pump and is hereinafter referred to as P Minimum pressurizing and shutoff valve 58 is disposed in line 54 and serves to positively block off fuel from the engine and has a dual function which is (1) to provide a minimum pressure to the control servo during initial starting and (2) to provide a positive fuel shutoff. Actuation of the minimum pressurizing and shutoff valve 53 is controlled by a switch over or windmill bypass and shutoff control valve which is generally indicated by numeral 69 and which will be described in more detail hereinafter. Minimum pressurizing and shutoff valve 58 comprises a chamber 62,

spring 64 and valve element 66. Spring 64 biases valve element 66 toward a closed position and the relative strength of this spring and the force responsive area of the valve element created by the pressure acting in chamber 62 determine the pressure in line 54 which is necessary for the opening of this valve.

The combined sensing and pressure regulating valve generally indicated by numeral 68 communicates with the upstream and downstream pressure of throttle valve 50 and serves to maintain constant the value of the pressure drop across the throttle valve. The operation of combined pressure regulating sensor and servo valve 68 is described as follows. A T-connectlion in line 54 leads to the valve 68 which includes chamber 76- and 72 which is separated by spool valve 74. Spool valve 74 includes on its opposite ends reaction surfaces 76 and 78 which respond to the forces created by the pressures acting in chambers 70 and 72, respectively, for movement of spool valve 74. Chamber 72 connects with the pressure up stream of throttle valve 5% via line 80 and chamber 76 connects with the pressure downstream of throttle valve 59 via, line 82 and the annular opening 84. Spring 86 biases spool valve '74- in a downward direction and the relative force of the spring and force responsive areas on the opposite ends of the spool valve 74 determines the position of spool valve 74 which in turn determines the pressure in chamber 88 of the pressure regulating valve 99. The value of the spring determines the value of the pressure drop of the throttle valve. As the pressure in chamber 70* increases, spool valve '74 moves downward permitting servo pressure P to communicate with chamber 88 via lines 91 and 92. Conversely, when pressure in chamber 7% decreases, spool valve 74 moves upward connecting chamber 88 with line '54 which is at a lower pressure than P The pressure regulating valve 94} which may be of any suitable type, is shown as having equal area reaction surfaces 98 and opposing each other so that the pressure in chamber 88 will be something less than the pressure in chamber 94 and the servo pressure in chamber 88 together with the strength of spring 96 determine the relative position of pressure regulating valve 90. For example, when the pressure in chamber 88 increases, the move-able valve element or servo motor 102 will be biased toward its closed position and conversely, when the pressure in chamber 88 decreases, the pressure in chamber 9% will urge valve element or servo motor 102 to its open position. Any fuel that is bypassed by the pressure regulating valve is carried back to the inlet of the pump via line 104. Valve 68 may include a fuel temperature compensator which varies the height of spring 86 in accordance with the temperature sensitive bimetal 1%. In order to obtain free movement of spool valve 74, the valve is continuously rotated by gear 1% which drives connecting link E181, pivotally connected to the spool valve '74-. It will be noted that this driving mechanism will not interfere with axial movement of the spool valve.

As mentioned above, the switch-over or windmill bypass and shutoff control valve 69 serves to control the pressure in chamber 62 of minimum pressurizing and shutoff valve 55. Valve 60 comprises chamber 112 and spool valve 114. The right-hand end of the spool valve has an enlarged diameter portion 1116 which seats against the inner portion on the right end of the bore 113. Spring 12%? biases the spool valve to the left, and the strength of this spring and force of the reaction surface of the right end of the spool valve urge the valve toward the closed position. Upon rotation of the pilot lever 122, cam 436 positions the spool valve 114 to the right against the spring 129 for simultaneously venting pressure P, in line 124 to chamber 62 and connecting chamber 88 to the drain pressure via line 92 and chamber 112. (Drain pressure is the lowest pressure of the fuel in the fuel control and will be hereinafter referred to as P,,.) In this manner, since the pressure in chamber 88 now equals drain pressure, the valve element 162, due to the force created in chamber 94, is placed in its open position, and servo pressure being higher than the pressure in line 54 causes valve element 6-6 to close. This is an important feature of this invention because this provides a method for preventing the fuel pressure in the fuel control from becoming excessive which, if not controlled, would inflict structural damages to the fuel control. This condition becomes most prevalent in the event that a malfunction in the engine occurs. As will be noted, the pump is continuously driven by the compressor even when the engine is inoperative due to windmilling effect caused by the air passing over the engines compressors. It should be noted that when spool valve 114 is moved to the right, high pressure P is simultaneously directed to chamber 62 of valve 53 closing valve element 66 thereby blocking oif fuel to the engine. By combining the shutoff valve with the windmill bypass feature, we are able to realize an efficient means for protecting the fuel control against the adverse effects created by windmilling without introducing a substantial increase in pressure drop across the fuel control which has heretofore been the situation of other windmill protection methods.

A check or relief valve 149 is connected across the pressure regulating valve sensor 6-8 and serves to prevent excessive fuel flow from reaching the engine in the event that the pressure regulator sensor 51 should fail. Lines 14-1 and 143 lead into lines 32 and 91 respectively for directing pressure across the ball 145 of check or relief valve 146. Spring 147 biases ball 145 to its closed position, and its value is slightly higher than the difference obtained by subtracting the value of spring 96 from spring 86. Thus during normal operating conditions, this valve is inoperative. However, should the pressure in line 143 exceed the force exerted by the spring 147, the flow will be shunted across valve 63 and hence, preventing the pressure in chamber 88 from increasing above this predetermined value. This results in preventing the pressure regulating valve 9-1 from shutting off and hence, causing all the flow in line 48 to be forced through valve 50. If valve 99 were to be closed in this manner, a substantial error in metered fuel would result, causing excessive damage to the engine.

The throttle valve 59 comprises a moveable valve element 150 having a piston head 152 forming one end of chamber 154. The servo pressure in chamber 154 is regulated for positioning the moveable valve element 152 which in turn defines the area of port 52 and as mentioned above, since the value of the pressure drop across this port is constant, each discreet position of the valve element 150 will deliver a predetermined quantity of fuel to the engine. The pressure in chamber 154 may be controlled by pilot valve 156. Pilot valve 156 is connected to drain pressure and high pressure via lines 158 and 160, respectively, and the relative movement of the spool valve 162 will connect the chamber 154 to either P or P pressure via line 164 depending whether it is moved to either the left or right. It will be noted that when the valve is in equilibrium, the port at the end of line 164 and the middle land 16-6 of spool 162 is on its line on line position. Movement of spool element 162 is imparted by multiplying linkage 168 which carries feedback spring 143 at its opposite end. The feedback spring 170 is connected to the valve element 156 for balancing out the forces on linkage 168 and nulling or balancing out the system.

The position of the multiplying linkage 168 reflects the product which resulted by multiplying the multiplicand as defined in the above by the compressor discharge pressure. A force proportional to compressor discharge pressure is applied at the free end of arm 17!} and the multiplication is effected as follows. Compressor discharge pressure is admitted internally of bellows 186 which has its free end engaging the top end of arm 170 and pivots about pivot point 182. A second bellows 184 opposes the movement of bellows 186 and is evacuated so that the relative movement of arm is a function of absolute pressure. interposed between the free end of arm 170 and multiplying linkage 168 are rollers 186 which vary the lever ratio of the multiplying linkage in order to effect a multiplication of the power plant operating variables or parameters as has been described above. The relative position of the rollers, as will be apparent, can be considered as the multiplicand which is proportional to the W /P ratio. Thus it is evident that the ratio W /P represents or is a function of the variables or parameters of the power plant which have been selected for proper power operation. A preferred selection of parameters is described herein, but it is pointed out that other parameters may be similarly utilized without departing from the scope of this invention.

Still referring to FIG. 2, rollers 186 are operatively connected to gas generator speed governor, compressor inlet temperature device, compressor inlet pressure device and the power lever in the manner immediately described hereinbelow. It will be noted that this fuel control provides for acceleration scheduling by utilizing the same signal generating mechanism with the exception of the power lever and compressor inlet pressure device as is utilized for steady state operation. Therefore, during acceleration regimes, the fuel flow as will be shown is made a function of speed of the compressor and the inlet temperature of the compressor and during steady state regimes, fuel flow is made a function of compressor speed, compressor inlet temperature, compressor inlet pressure and power lever position.

Rollers 186 are attached to reciprocal arm 188 which in turn is connected to horizontal leg 190 of bell crank 192. It will be noted that the vertical arm 194 of the bell crank is shown as being out of engagement with the cam 198 but being in engagement with cam 20b. The purpose of vertical arm 194 is to override the effect of cam 260 by lifting arm 190 off cam 200 when the lower end of arm 194 comes into contact with the three-dimensional cam 198 which occurs during the acceleration regimes. It is therefore evident that cam 260 is designed to schedule the fuel flow for steady state power plant operating conditions while the override feature just described provides a schedule for limiting fuel flow during acceleration regimes of power plant operations. The three-dimensional cam will be described in more detail hereinafter.

The method of obtaining the value of the multiplicand can best be described as follows. Rotating the power lever 122, cam 210 which is connected thereto by shaft 212 rotates correspondingly and schedules the desired speed for each discreet angle of power shaft position. Cam 210 is of the three-dimensional type which can be totaled as well as translated along shaft 212. The cam may be contoured to schedule compressor inlet pressure signal which biases the set or desired speed signal in accordance with the compressor inlet pressure sensed at the power plant. This is accomplished as follows. Compressor inlet pressure is admitted to the sealed chamber 226 via line 222 and is sensed by evacuated bellows 224 whose free end engages the left end of lever 226 which is pivotally secured to member 228. A spring 230 balances evacuated bellows 224 and in accordance with the pressure in chamber 2211 contracts and expands for relative m0ve ment of lever 226. It is evident that relative movement of lever 226 is a function of the absolute pressure. Lever 226 is operatively connected to pilot valve 249 which in turn controls servo motor 242 for biasing the speed set cam. By displacing spool 244, P pressure in line 246 is admitted to either chamber 248 or chamber 250 of the servo motor 242 via line 252 or 254. Simultaneously, the chamber which is not subjected to P pressure is vented to drain pressure. Spring 256 balances spool 244 against the free end of arm 226. The pilot valve may be rotated in the same manner as was described in connection with the pressure regulating valve sensor 68. For convenience, the connections for rotating all of the pilot valves have been shown schematically and may be mechanically connected to speed governor 400.

As mentioned above, by actuation of pilot valve 240, servo motor 242 will make a proportionate movement causing connecting rod 250 to move upwardly or downwardly and in turn rotating linkage member 261 about its pivot point 262. The bifurcated end 264 of linkage member 261 engages roller 265 of connecting rod 260. A T-linkage 270 mechanically connects linkage member 261 to cam 210 for proportional translation of this cam in accordance with the signal generated by the movement of lever 226. Spring 272 carried on the free end of horizontal arm 274 of T-linkage 279 serves to balance the forces acting on lever 226 for nulling or balancing out the servo system. That is to say, when cam 210 is in the position corresponding to the signal produced by movement of arm 266, the lands of spool 244 will be in their line-on-line position with their cooperating ports. The left end of follower 2% is pivotally connected intermediate the ends of vertical arm 292 which is pivotally supported to the left end of horizontal lever 294 which in turn pivots around pivot connection 2% of bell crank 29%. Movement is imparted to adding bar 3% by rotating lever 290 about pivot point 382 for up and down movement of vertical arm 292. It will be noted that the bottom end of vertical arm 292, carries a roller 3% which rides along the surface of cam 308. The relative angle that this cam makes with vertical arm 232 is adjusted by external connections 31% and 312. These adjustments function to calibrate the fuel control for different engine operation schedules.

From the foregoing, it is apparent that the position of horizontal lever 294 is proportional to the desired or set speed as scheduled by the pilot lever 122.

The set speed may be modified in accordance with compressor inlet temperature by designing a schedule in the profile of the three-dimensional cam 198. In order to build in a temperature scheduled signal for each desired speed setting, the three-dimensional cam is made to rotate and translate within its cylinder 332. The means for accomplished rotation will be described hereinafter in connection with FIGS. 3 and 4. The method of resetting the set or desired speed in accordance with the temperature can be best explained as follows. T-linkage 314, which is pivotally supported to member 316, engages the cam by the follower arm 318. Follower arm 318 in turn transmits motion which is proportional to the profile of cam 198, to horizontal lever 294 by bell crank 298 which is pivotally supported to pivot 320. It will be noted that torsion spring 322, which engages both shaft 324 and cam 200, serves to keep the connecting members in engagernent.

The purpose of adding bar 300 is to compare the desired or set speed signal with a signal proportional to the actual compressor speed and to feed to rollers 186 a signal which is proportional to the difference or error of these two signals for providing the value of the multiplicand as will be more fully described hereinbelow.

It will be noted that the position of the right-hand end of adding bar 199 is equilivant to the ratio W /P. The actual speed signal is fed into the adding bar at pivot point 328 which is positioned by the three-dimensional cam 198, which in turn is controlled by gas generator speed governor 330. In the assembly of this fuel control, the three-dimensional cam 198 is inserted into housing 332 such that each discreet axial position thereof corresponds to a definite speed value of speed governor 330. That is to say, for a definite N,;, the three-dimensional cam 198 will be at a predetermined position. The speed governor, which is driven by the compressor in any suitable manner, has fiyweights 334 rotatably connected to drive gear 336 which is attached to base 338. Flyweights 334 are pivotally supported to the base 338 and rotates about pivot point 340 as a function of the centrifugal force exerted thereon. Rotation of flyweights 334 will impart axial 8 movement to spool 342 of pilot valve 344. Spring 346 serves to balance spool 342 against the force exerted by flyweights 344. When the speed governor senses an overspeed, for example, centrifugal force causes the fiyweights to upset the balance exerted by spring 346 as a result of the fiyweights pivoting about point 349, and forces spool valve 3 -2 in an upward direction. This connects P pressure in line 348 to chamber 350 via line 352 and communicates chamber 354 with drain pressure via line 356, translating three-dimensional cam 198 in a downward direction. Conversely, during an underspeed condition, the fiyweights 334 tend to pivot inwardly toward the center line of driving gear 336 allowing spool 342, under the influence of spring 346, to move downwardly. Thus, chamber 354 communicates with P via line 356 and chamber 358 communicates with P via line 352 causing cam 113 to move in an upward direction. This motion is transmitted to adding bar 300 at connecting point 370.

From the foregoing, it is apparent that this point repre sents or is a function of the actual N and the point where horizontal lever 294 contacts bar 390 represents or is a function of the desired or set speed. When the values of these points differ, adding bar 300 is caused to rotate about pivot point 372 which in turn will cause cam 200 to rotate around shaft 324 causing the horizontal leg of bell crank 192 to move in an upward or downward direction. The effect of this movement of these inkages is to feed the multiplicand signal W /P to the rollers for multiplication by the compressor discharge pressure signal for proper positioning of throttle valve 50. The system will return to equilibrium when spring 346 is again restored to its original height by movement of feedback lever 443 which engages this spring at its left end for balancing the force exerted by flyweights 334. By proper contouring of the profile of cam 200, it should be understood that a minimum W /P ratio may be built into the fuel control (see FIG. 7). An important feature of this invention is the fact that the three-dimensional cam serves as a piston, i.e. the piston and cam are made integral. It should be noted that the working or reactive surfaces 360 and 362 are designed as piston heads of a usual doubleacting piston for reciprocation cylinder 332. The integral piston and cam 19% is particularly located in this position so that it can be easily reached from the outside of the housing of the fuel control. Cap 364 located at the bottom of cylinder 332 is threadably engageable with the cylinder housing. By removing cap 364, cam 198 can be easily reached externally of the fuel control casing so that by unfastening nut 366 threaded to the bottom of connecting rod 368, cam 198 can easily be detached.

We have found that it is possible to vary the droop of the scheduled fuel flow for a given speed by superimposing on profile 382 of cam 193 a preselected droop schedule. Droop is defined, for purposes of this invention, as the rate of change of fuel fiow for a unit change of speed. This can be best explained by referring to the graph of FIG. 7 which shows the W /P ratio plotted against N Line A represents steady state power plant operating conditions and lines B, C, D, and E represent a family of droop lines which intersect steady state line A at a point indicative of the proper steady state operating speed. The purpose of contouring the profile 382 is for varying the slope of these droop lines thus, as was mentioned above, since each position of the cam represents a particular speed, by proper modification of the cam, the slope of the droop lines can be varied as a function of speed. In this manner the engine dynamic response can be adjusted for optimum performance over a wide range of operating speeds. Should the speed, for any reason, deviate from the point represented by the intersection mode between the steady state line and droop line, the control will restore the engine to its proper operating speed by following its particular droop line.

Referring again to FIG. 2, it will be noted that the valve element 153 of throttle valve 55 carries with it an axial extension 386 which abuts against adjusting screw 388 which serves to provide an adaptable setting for the minimum flow of fuel capable of passing through the throttle valve. It is further necessary, for proper operation of the control, to provide for a minimum W /P ratio which may be obtained by contouring the top surface 396 or" cam 2% so that its radius of curvature becomes constant for a span where the minimum Wf/Pg ratio is desired.

In order to attain rotation of the three-dimensional cam 198 in response to compressor inlet temperature, as shown in FIG. 4, a liquid-filled bellows 4% is provided in chamber 402 which is connected to the engines compressor inlet by line 464. An ejector pump 263 may be connected to compressor discharge pressure (not shown) is disposed downstream of the bellows for inducing flow through chamber 4-02, assuring that the air around the bellows does not stagnate and give an inaccurate signal. Variation in bellows 4% causes arm 40S attached to its free end to move up or down which in turn causes cam 410 to pivot about shaft 412 for corresponding movement of spool valve 41.4 of pilot valve 416. Movement of the spool valve 414 connects pressure reacting chambers 42%) and chamber 422 of servo motor 424 to either P or P, pressure. Variation of pressures in chambers 422 or 424 will cause the piston 426 to move either to the lift or to the right. An important feature of this invention is the manner in which the cam is arranged with its cooperating parts which provides a simplified method for nulling or balancing out the effect of the temperature signal. It will be noted that as the piston 426 translates, the bottom surface of the cam 41%? presses against roller 439 which is pivotally secured to arm 432. This provides a feedback signal to the pilot valve for nulling out or restoring the system back to equilibrium. Because of this particular arrangement, the profile of the bottom of cam 272 may easily take any shape thus providing means for imparting a linear or nonlinear output signal as may be desired. As shown in FIG. 3, piston 426 of servo motor @2 1 carries a rack gear 299 which engages with the gears located on the bottom of three-dimensional cam 142 for rotation thereof. It will be noted that the teeth on three-dimentional cam 142 span an axial distance which is sufficient to keep the teeth in engagement throughout the length of travel of the cam 193.

Operation Upon rotation of the pilot lever 1.22 for initial starting, cam 43%} urges spool valve 114 of windmill bypass and shutoff valve 69 to the right which simultaneously connects chamber as of minimum pressurizing and shutoff valve 58 to drain pressure and putting chamber 83 of pressure regulating valve 99 in communication with the pressure in line 54 via lines 9!) and 92. When the pressure in line 38 increases to a value above both the drain pressure and the force exerted by spring 66 in chamber 62, the shutoif valve will open allowing fuel to be ejected into the engine. Simultaneous with this movement, three dimensional cam 210 sets the position of horizontal arm 294 to the desired speed setting. This in turn causes adding bar 330 to rotate about pivot 372 which in turn forces the right-hand end of adding bar 3% to engage with cam 2% for rotation thereof which adjusts the height of the horizontal leg 14% of bell crank 194 for setting the position of rollers 186. The rollers in turn press against both multiplying link 168 and lever 117i) for relative movement of pilot valve 156 for controlling the pressure in chamber 154 for positioning throttle valve 34 and hence meter the proper quantity of fuel to the engine. Since the rollers represent the W /P ratio which is the multiplicand and since lever 170 is a function of compressor discharge pressure it is evident that the formula W /PXP=W is satisfied.

It should be noted that an acceleration schedule may be incorporated in this control and is scheduled by the proper contouring of profile 440 of cam 142. Since this cam translates and rotates as a function of both compressor inlet temperature and compressor speed, the acceleration schedule will therefore be a function of both speed and temperature. Should the engine go beyond the temeprature or speed which is predetermined by threedimensional cam, arm 1% will engage the cam causing bell crank 192 to pivot about point 442 which in turn lifts the horizontal leg 1% of hell crank 192 off of the steady state cam 169 for repositioning rollers 186 which in turn adjust throttle valve in the manner described in the above for decreasing the quantity of fuel delivered to the engine. As the engine speed increases to the desired speed, adding bar 3% through the linkage 443 will reset the height of spring 346 so as to balance the forces exerted by the flyweights 334 in order to maintain steady state operations. The selected engine parameters will continuously scrutinize engine operating conditions for continuously maintaining the proper W /P ratio.

Referring to FIG. 5, a version of the fuel control of this invention is illustrated for adaptation to a helicopter. Since the fuel control for the turbojet just described is identical to the fuel control for helicopter use, for convenience the repetition of several major components will be omitted. In controlling a helicopter, the N is sensed and utilized as the main controlling element while the N is sensed and is utilized as a topping governor and control during ground idle aircraft maneuvers. For adaptation to the fuel control, cam 5% is secured to shaft 324 of the cam 2%. It will be noted that for normal control operation, that is, as long as the N governor 516 is regulating, adding bar 3% will be out of engagement with horizontal bar 294%, hence it will be seen that although the gas generator governor 330 is continuously sensing the speed of the compressor, it will have no effect on the multiplicand while the free turbine governor does the primary controlling. However, it should further be noted that the acceleration cam will still operate as previously described in order to override the free turbine governor signal during acceleration conditions. The free turbine desired speed is set by movement of power lever 5% which positions cam 510 carried by shaft 512 which in turn positions link 514. The free turbine speed governor 516 operates in substantially the same manner as the gas speed generator and may be identical thereto and for convenience, a description thereof will be omitted. Pilot valve 518, which is operatively connected to speed governor 516, regulates the pressure in chambers 52% and 522 for positioning of piston 541 of servo motor 524. This in turn raises and lowers connecting rod 526 for movement of cam 528 which is pivotally secured thereto by link 542. Therefore, it is apparent from the foregoing that the position of cam 528 is a function of the actual speed sensed by governor 516. Feedback mechanism, comprising of lever arm 530 and spring 532, serves to return the servo system back to equilibrium.

It may be desirable, for stability purposes, to bias the speed error signal which is taken off cam 528 by compressor inlet temperature and N This is accomplished by connecting the speed follower lever 534 directly to the three-dimensional cam 198. The collective pitch signal, which is taken off the collective pitch lever 21, may be incorporated to bias the position of cam 5th) by varying the position of lever 55). Movement of link 538 imparts rotation to cam 500 by bell crank 552 which in turn positions the horizontal leg 1% of bell crank 192 for adjustment of rollers 186 (see FIG. 2), and hence controls the throttle valve in the manner described above.

In the case of turboprop control for a propeller-driven engine, the major elements for the helicopter control are in the main identical and a mere elimination of several component parts are all that is required for conversion to a control for propeller-driven aircraft. It should be understood that the propeller governor varies the pitch of the usual variable pitch blade which serves to maintain the propeller at a constant speed. Since the propeller governor does the primary controlling, the free turbine governor merely acts as a topping control. A theoretical explanation of propeller control is not deemed necessary to the understanding of this invention but a description could be had by referring to US. Patent No. 2,822,666 supra. The linkage of the turboprop control may be identical to the helicopter linkage, and a description of the common component parts will be omitted for convenience. It will be noted that cams 528 and Still are substantially the same as shown in FIG. 4 to the ones shown in FIG. 3. Since the free turbine governor merely acts as a topping governor, it is not necessary to bias the speed signal with temperature and compressor gas generator speed. As the pilot lever 503 is rotated, arm 410 adjusts linkage 514 in a similar manner as was described in connection with the control for the helicopter. This serves to set cam Silt? via bell cranks 560 and 552, lever 556 and link 5:32 to a value above the setting of the gas generator speed governor 3%. Of course, the actual speed of the free turbine speed governor Silo is taken off cam 528 in the manner described above. It will be noted that in this control the right-hand end of adding bar 3% is in contact with horizontal lever 2% for controlling the throttle valve in the manner described in connection with the fuel control shown in FIG. 2.

What has been shown by this invention is a simplified hydromechanical fuel control which is easily adaptable to turbojet as well as turboprop engines and lends itself to being adaptable for different engines. Due to the fact that the three-dimensional cam is positioned in a particular relationship to the adding bar, it has been made possible to easily detach this cam without disturbing the settings of any of the other controlling elements, and further, lend itself for easy retraction from the fuel control housing. The three-dimensional cam has been utilized to its utmost advantage by integrating it with the double-acting piston, another reason for simplifying this fuel control. In this control, the normal pilot valve has been adapted to become a combination pilot-type valve and pressure sensor control. An integral feedback system has been adapted to the temperature servo valve in a unique manner which lends itself to compactness and simplicity. A further feature of this servo device is that this particular arrangement can easily be adapted for converting an input signal to a linear as Well as a nonlinear output signal. Means have been provided for preventing against destruction of the fuel control due to windmilling effects without introducing a substantial increase to the total pressure drop across the fuel control. In addition, a check valve shunting the flow across the pressure regulating valve sensor has been utilized in a novel manner to protect the engine from surging and/or overheating in the event of pressure regulating valve sticking.

It should be understood that the invention is not limited to the particular embodiments shown and described herein, but that various changes and modifications may be made without departing from the spirit or scope of this novel concept as defined by the following claims.

We claim:

1. In a combined cam and piston device comprising a housing defining a cylindrical bore, a piston mounted in said cylindrical bore being movable in a reciprocating and rotating direction and having at least one cam surface extending longitudinally thereof, side openings in said housing allowing communication with said bore, follower means adapted to pass through said openings for engagement with said cam surface, and means for imparting rotary and reciprocal motion to said piston.

2. In a servo motor device, the combination comprising a housing defining a piston chamber, a piston disposed in said chamber and defining pressure chambers located on opposite ends of said piston, a first reaction surface disposed on an end of said piston and defining a first working area, a second reaction surface on the opposite end of said piston defining a second working area, a cam integrally connected to said piston and located intermediately of said first and second reaction surfaces, said cam movable in a linear direction and transversely of said direction, said cam comprising at least one cam profile surface extending longitudinally of said piston and spaced from said reaction surfaces, cam follower means adapted to pass through an opening in said housing to engage said cam profile surface, and means for imparting motion to said piston to move it in a linear direction and transversely of said direction.

3. In a control devce, a cylinder having a port at least at one end for the admission of control fluid thereto, a piston in the cylinder axially movable in response to pressures of said control fluid acting on the end surface, of said piston, means for turning the piston within the cylinder, said piston having cam surfaces on the side walls thereof spaced from said end surfaces, and follower means engaging with said cam surfaces, and said cylinder having openings in the side wall to receive the follower means.

4. In a combined cam and piston device comprising a housing defining a cylindrical bore, a piston mounted in said cylindrical bore being movable in a rotating and reciprocal direction and having a pair of reaction surfaces formed at the opposite ends thereof, and disposed in said bore so as to define a pair of reaction chambers each in communication with one of said reaction surfaces, fluid connections adapted to deliver fluid pressure in each of said chambers for linear movement of said piston, first and second side openings in said housing providing external communication with said bore, first and second cam surface extending longitudinally and spanning a circumferential portion of the periphery of said piston spaced intermediate the ends of said reaction surfaces, follower means adapted to pass through said first and second side openings for engagement with said cam surfaces, and means for imparting rotary motion to said piston.

5. A servo system having a cylinder including at least one port adapted to admit control fluid, a pilot valve having valve stem means extending into said cylinder and having fluid connections connecting said cylinder to said valve for metering said control fluid, a piston disposed in said cylinder defining at least one chamber for receiving said control fluid and axially movable in response to the pressure in the chamber, a cam disposed in said cylinder pivotally supported to the piston and operatively connected to said valve stem means, a signal generating device adapted to position said cam in accordance with said signal whereby movement of said cam will impart a corresponding movement to said piston pilot valve for efiectuating movement of said piston.

6. A servo system having signal generating means for imparting an input signal including a first member, a servo motor having first and second end reaction surfaces, a control valve for controlling said servo motor means, a pivotable member between said first and second end reaction surfaces operably connecting said first member and control valve, and means on said pivotable member responsive to the position of the servo motor for varying the effect of the control valve.

7. In a servo system, a cylinder having a first and sec ond port disposed at opposite ends thereof, a control valve including fluid connections communicating with said ports, a piston in the cylinder defining opposing chambers communicating with each of said ports and axially movable in response to the pressures in said chamber, said piston comprising a pair of axially spaced apart reaction surfaces including a member pivotally mounted intermediate thereof and movable in a direction transversely of said piston, signal generating means cooperating with said member for imparting an input signal to said control valve, and said member responsive to the movement of said piston for varying the effect of said control valve.

8. In a servo system, a cylinder having at least one port for admittance of control fluid, a piston axially movable in response to the pressure of said fluid, a control valve controlling said piston and having fluid connections communicating with said port, means responsive to a temperature variation for producing an input signal, a cam pivotally mounted on said piston adapted to receive said signal for positioning said control valve, a movable mem ber, means connecting said piston to said member for positioning said member in accordance with the position of said piston, and feedback means carried by said cam for varying the effect of said control valve.

9. In a servo system as defined in claim 8, wherein a rack gear is mounted on said piston and said connecting means comprises a gear mounted on said movable member and engageable with said rack gear.

10. A servo motor and control therefor comprising, in combination, a housing defining a cylindrical bore, a piston disposed in said cylindrical bore having an elongated member, a pair of axially spaced reaction members supported by said elongated member radially extending to the inner wall surface of the cylindrical bore defining a pair of opposing fluid receiving chambers, a pilot valve casing mounted adjacent said housing including a valve stem supported therein, said valve stem extending through an opening in said housing and terminating in said cylindrical bore at a point intermediate said pair of reaction members, fluid connecting means interconnecting said valve casing and said pair of fluid receiving chambers, lands carried on said valve stem adapted to lead fluid through openings in said valve casing through said connecting means into and out of said fluid receiving chambers for positioning said piston longitudinally, a pivotable member pivotably supported to said elongated member intermediate said pair of reaction members and adapted to engage the end of said valve stem, and means for generating an input signal including a motion transmitting member extending through an opening in said housing and engaging a surface of said pivotable member whereby said pivotable member positions said valve stem for moving said lands relative to said openings in said valve housing.

11. Apparatus as claimed in claim 10 wherein said valve stem is located diametrically opposite said motion transmitting member.

References Cited in the file of this patent UNITED STATES PATENTS 1,001,989 Rowntree Aug. 29, 1911 2,297,213 Gosslad et a1. Sept. 29, 1942 2,643,055 Sorteberg June 23, 1953 2,816,562 Dyson Dec. 17, 1957 2,867,233 Adelson Jan. 6, 1959 2,980,069 Hilker et al Apr. 18, 1961 FOREIGN PATENTS 387,567 Great Britain Feb. 9, 1933 UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTIQN Patent No 3,129.643 April 21, 1964 Robert D, Porter et ale It is hereby certified that error appears in the above numbered patent reqiiring correction and that the said Letters Patent should read as corrected below.

Column 11 line 66, after "allowing" insert external column 12, line 12, for devce" read device y line 50, strike out "piston"; line 55, strike out "means",

Signed and sealed this 4th day of Angnstf1964,

(SEAL) Attest:

ERNEST W. SWIDER EDWARD 'J. BRENNER Altcsting Officer Commissioner of Patents 

8. IN A SERVO SYSTEM, A CYLINDER HAVING AT LEAST ONE PORT FOR ADMITTANCE OF CONTROL FLUID, A PISTON AXIALLY MOVABLE IN RESPONSE TO THE PRESSURE OF SAID FLUID, A CONTROL VALVE CONTROLLING SAID PISTON AND HAVING FLUID CONNECTIONS COMMUNICATING WITH SAID PORT, MEANS RESPONSIVE TO A TEMPERATURE VARIATION FOR PRODUCING AN INPUT SIGNAL, A CAM PIVOTALLY MOUNTED ON SAID PISTON ADAPTED TO RECEIVE SAID SIGNAL FOR POSITIONING SAID CONTROL VALVE, A MOVABLE MEMBER, MEANS CONNECTING SAID PISTON TO SAID MEMBER FOR POSITIONING SAID MEMBER IN ACCORDANCE WITH THE POSITION OF SAID PISTON, AND FEEDBACK MEANS CARRIED BY SAID CAM FOR VARYING THE EFFECT OF SAID CONTROL VALVE. 